Multi-speed transmission in planetary design

ABSTRACT

A planetary multi-speed transmission for a vehicle with a housing is proposed. A first shaft is provided as a drive (An) and a second shaft is provided as an output (Ab) and is arranged axially parallel to the drive. Three planetary gear sets and additional shafts, along with six shifting elements are provided, through which the actuation of several gears are realized. Machine elements are provided for transfer of torque between the drive (An) and the output (Ab). The first shaft is connectable, as drive (An) to the planetary gear carrier of the first planetary gear set, to the sun gear of the second planetary gear set, to the ring gear of the first planetary gear set, to the planetary gear carrier of the second planetary gear set and to the first spur gear stage. The second shaft is connected or connectable, as a drive (Ab), to the first machine element and to the second machine element.

FIELD OF THE INVENTION

The present invention relates to a multi-speed transmission in planetarydesign for a vehicle with a housing, whereas a first shaft is providedas a drive (An) and a second shaft (2) is provided as an output (Ab)that is arranged in a manner axially parallel to the drive, whereasthree planetary gear sets and additional shafts, along with six shiftingelements are provided, through which the actuation of several gears arerealized, and whereas machine elements (ST1, ST2) are provided fortransfer of torque between the drive (An) and the output (Ab).

BACKGROUND

As an example, publication DE 10 2007 014 150 A1 discloses aload-shiftable multi-speed transmission. With the multi-speedtransmission, the drive shaft is firmly connected through a torsionalvibration damper to a first shaft of a first shaft train. A second shafttrain arranged parallel to this includes, among other things, the twooutput shafts designated as shafts. The two shaft trains are connectedto each other through three spur gear stages. A first three-shaftplanetary gear stage is located on the first shaft train. A secondplanetary gear stage and a third planetary gear stage are located on thesecond shaft train. Thus, the multi-speed transmission comprises tenshafts that are connected to each other through three spur gear stagesand three planetary gear stages. For shifting the eight forward gearsand one reverse gear, five shifting elements are necessary. The providedshifting elements are hydraulically operated.

In order to reduce hydraulic losses, the shifting elements are to bearranged in a manner that is easily accessible from the outside.However, with a front-transverse installation of the transmission in avehicle, only a limited axial installation space is available.

SUMMARY OF THE INVENTION

The present invention is subject to the task of providing a multi-speedtransmission with the highest possible number of gears and an easyaccessibility of the shifting elements, with, at the same time, a goodgearing efficiency and a need for axial installation space that is aslow as possible. Additional objects and advantages of the invention willbe set forth in part in the following description, or may be obviousfrom the description, or may be learned through practice of theinvention.

This task is solved by the transmission embodiments described andclaimed herein.

Accordingly, a load-shiftable multi-speed transmission in planetarydesign, or a multiple-gear planetary transmission for a vehicle with ahousing, is proposed, whereas the drive or the drive shaft, as the casemay be, and the output or the output shaft, as the case may be, arearranged in a manner that is axially parallel to each other for apreferred front-transverse installation. The multi-speed transmission inaccordance with the invention comprises only nine shafts, threeplanetary gear sets and only six shifting elements, in order to realizeat least nine forward gears and one reverse gear. In addition, for thecoupling of the drive and the output, it is preferable that only twomachine elements are provided.

Given the fact that the first shaft, as a drive, is detachably connectedor connectable to the planetary gear carrier of the first planetary gearset, to the sun gear of the second planetary gear set, to the ring gearof the first planetary gear set, to the planetary gear carrier of thesecond planetary gear set and to the first spur gear stage and that thesecond shaft, as an output, is connected, or is detachably connected orconnectable, to the first machine element and to the second machineelement, a multi-speed transmission in accordance with the inventionthat enables an actuation of the shifting elements that improves thedegree of efficiency and is thus in line with demand arises, whereas theadvantageously low number of transmission elements of the multi-speedtransmission for a front-transverse design has its transmission elementsnested with each other in such a manner that an arrangement thatparticularly saves axial installation space is enabled. In addition tothe improved degree of efficiency, low component stresses and lowconstruction costs arise.

The easy accessibility of the shifting elements may be realized, amongother things, on the one hand through the use of brakes as shiftingelements and, on the other hand, through the use of clutches as shiftingelements, which are preferentially positioned at outside shafts,preferably at the drive and at the output, with the multi-stagetransmission in accordance with the invention. Due to the lowconstruction costs, in an advantageous manner, low production costs anda low weight of the multi-speed transmission in accordance with theinvention arise.

Within the framework of a possible embodiment of the invention, it canbe provided that, as a machine element for the coupling or for thetransfer of torque between the drive and the output, at least one spurgear stage or the like, which realizes the transmission ratio for theoutput differential, is used. Preferably, only two machine elements orspur gear stages are provided. However, other machine elements for thetransmission of torque power, such as chains, belts or the like, may beused.

Viewed in an axial direction, the planetary gear sets are arranged inthe order of first planetary gear set, second planetary gear set andthird planetary gear set, whereas it is preferable that only negativeplanetary gear sets are provided. However, at spots where the bindingability allows it, individual or several negative planetary gear setsmay be converted into positive planetary gear sets, if, at the sametime, the bar connection or planetary gear carrier connection and thering gear connection are exchanged, and the amount of the stationarytransmission ratio is increased by the value of 1. As is well-known, anegative planetary gear set features, at the planetary gear carrier,rotatably mounted planetary gears, which mesh with the sun gear and thering gear of such planetary gear set, such that, with a planetary gearcarrier that is held down and a rotating sun gear, the ring gear rotatesin a direction opposite to the direction of rotation of the sun gear. Asis well-known, a positive planetary gear set features, at its planetarygear carrier, inner and outer planetary gears that are rotatably mountedand are in a tooth meshing with each other, whereas the sun gear of suchplanetary gear set meshes with the inner planetary gears, and the ringgear of such planetary gear set meshes with the outer planetary gears,such that, with a planetary gear carrier that is held down and arotating sun gear, the ring gear rotates in the same direction as thedirection of rotation of the sun gear.

With the multi-speed transmission in accordance with the invention, ahydrodynamic torque converter or a hydrodynamic clutch can be used asthe start-up element. It is also conceivable that an additional start-upclutch or an integrated start-up clutch or a start-up brake are used.Furthermore, it is possible that an electric machine or any other powersource is arranged at at least one of the shafts. Moreover, at at leastone of the shafts, a freewheel is arranged for the housing or foranother shaft.

Preferably, with the multi-speed transmission in accordance with theinvention, nine forward gears and at least one reverse gear can beshifted by means of the provided shifting elements. However, it isconceivable that, preferably for the fourth forward gear and also forother gears, additional shifting combinations are made possible bycombining other shifting elements.

The term “shifting element” is understood to mean a shiftable connectionbetween two elements of the transmission, whereas the torque to betransferred between such two elements is transferred by means of theforce closure or frictional closure or by means of the form closure. Ifboth elements of the shiftable connection are designed to rotate, theshifting element is referred to as a clutch, and if only one of the twoelements of the shiftable connection rotates, the shifting element isreferred to as a brake. Moreover, the geometric position and/or order ofthe individual shifting elements can be freely selected, as long as thebinding ability of the elements allows this. In this manner, individualelements may be arbitrarily moved into any position. In addition, to theextent permitted by the external shape, several gear sets can bearranged radially above one another, thus in a nested manner.

Embodiments of a force-fitting shifting element include multi-diskclutches or brakes, band brakes, cone clutches or brakes,electromagnetic clutches, magnetic powder clutches andelectro-rheological clutches. Embodiments of a positive-locking shiftingelement include claw clutches or brakes and tooth clutches.

Thus, in general, both frictional-locking and positive-locking shiftingelements may be used as shifting elements. Preferably, given itscharacteristics, in particular the fourth shifting element designed as aclutch can be designed as a claw shifting element, by which significantconsumption advantages can be achieved.

BRIEF DESCRIPTION OF THE DRAWINGS

In the following, the present invention is explained in more detailbased on the drawing. The following is shown:

FIG. 1 is a schematic view of a first design variant of a multi-speedtransmission in accordance with the invention;

FIG. 2 is a schematic view of a second design variant of the multi-speedtransmission; and

FIG. 3 is a shifting diagram for the various design variants of themulti-speed transmission.

DETAILED DESCRIPTION

Reference will now be made to embodiments of the invention, one or moreexamples of which are shown in the drawings. Each embodiment is providedby way of explanation of the invention, and not as a limitation of theinvention. For example features illustrated or described as part of oneembodiment can be combined with another embodiment to yield stillanother embodiment. It is intended that the present invention includethese and other modifications and variations to the embodimentsdescribed herein.

Each of FIGS. 1 and 2 shows an example of a design variant of themulti-speed transmission in planetary design in accordance with theinvention, for example as an automatic gearbox or automatic transmissionfor a vehicle.

Regardless of the particular design variants, the multi-speedtransmission comprises a merely schematically indicated housing 11, witha first shaft 1 as a drive An and a second shaft 2 as an output Ab thatis arranged in a manner axially parallel to the drive, along with sevenadditional shafts 3, 4, 5, 6, 7, 8, 9. Furthermore, a first planetarygear set RS1, a second planetary gear set RS2 and a third planetary gearset RS3 are provided, which are preferably designed as negativeplanetary gear sets. For shifting several gears, a first shiftingelement K1 designed as a clutch, a second shifting element K2 designedas a clutch, a third shifting element K3 designed as a clutch, a fourthshifting element K4 designed as a clutch, a fifth shifting element B1designed as a brake, and a sixth shifting element B2 designed as a brakeare provided.

For the coupling or for the transfer of torque between the drive An andthe output Ab, two arbitrary machine elements are preferably provided;with the design variants, these are designed, for example, as a firstspur gear stage ST1 and a second spur gear stage ST2. With the firstdesign variant in accordance with FIG. 1, the first spur gear stage ST1comprises a fixed gear 12, which is connected to the fifth shaft 5, andan idler gear 13 in a meshing with this, which is connected through theninth shaft 9 and through the fourth shifting element K4 to the secondshaft 2. The second spur gear stage ST2 comprises a fixed gear 14, whichis connected to the sixth shaft 6, and a fixed gear 15 in a meshing withthis, which is connected to the second shaft 2. In contrast to the firstdesign variant, with the second design variant in accordance with FIG.2, the first spur gear stage ST1 comprises an idler gear 12A, which isconnectable through the ninth shaft 9 and the fourth shifting element K4designed as a clutch to the fifth shaft 5. The idler gear 12A is in ameshing with a fixed gear 13A, which is connected to the second shaft 2.

With respect to the connection options between the provided shafts 1, 2,3, 4, 5, 6, 7, 8, 9, the provided three planetary gear sets RS1, RS2,RS3, the provided housing 11 and the provided shifting elements K1, K2,K3, K4, B1, B2 along with the provided spur gear stages ST1, ST2, withthe term “connectable”, it is to be understood that the describedelements are detachable (for example, connected by a shifting element),such that the connection is locked with an activated shifting elementand open with a non-activated shifting element. The detachableconnection may be realized through, in addition to the shifting element,an additional element such as a shaft or the like. The term “connected”is understood to mean that the described elements are connected to eachother in a manner that is virtually fixed, thus not detachable. A director indirect fixed connection (for example, through additional elements)may be realized.

In accordance with the invention, it is provided with the multi-speedtransmission that the first shaft 1 is detachably connected orconnectable, as drive An, to the planetary gear carrier PT1 of the firstplanetary gear set RS1 and the sun gear SR2 of the second planetary gearset RS2. Furthermore, the first shaft 1 is connectable to the ring gearHR1 of the first planetary gear set RS1. Moreover, the first shaft 1 isconnectable to the planetary gear carrier PT2 of the second planetarygear set RS2 and the first machine element or the first spur gear stageST1. Depending on the design variant, the second shaft 2 is connected orconnectable, as output Ab, to the first machine element or the firstspur gear stage ST1, as the case may be, and the second machine elementor the second spur gear stage ST2, as the case may be.

With the first design variant in accordance with FIG. 1, the secondshaft 2 is connected to the fixed gear 15 of the second spur gear stageST2. Furthermore, the second shaft 2 is connectable through the fourthshifting element K4 designed as a clutch and through the ninth gear 9 tothe idler gear 13 of the first spur gear stage ST1.

With the second design variant in accordance with FIG. 2, the secondshaft 2 is directly and firmly connected to the fixed gear 13A of thefirst spur gear stage ST1 and to the fixed gear 15 of the second spurgear stage ST2. The idler gear 12A of the first spur gear stage ST1 isdetachably connected or connectable through the ninth shaft 9 andthrough the fourth shifting element K4 designed as a clutch, and throughthe fifth shaft 5 and through the third shifting element K3 designed asa clutch, to the first shaft 1. Furthermore, the first spur gear stageST1 is connectable through the ninth shaft 9 and through the fourthshifting element K4 designed as a clutch, and through the fifth shaft 5,to the planetary gear carrier PT2 of the second planetary gear set RS2.

With the equally effective transmission variant in accordance with FIG.2, the fourth shifting element K4 designed as a clutch, which connectsthe first spur gear stage ST1 to the output shaft or to the second shaft2, is positioned on the other side of the spur gear, thus on the side ofthe transmission input shaft or the first shaft 1. For this purpose, theoriginal fixed gear 12 is the idler gear 12A and the original idler gear13 is the fixed gear 13A.

With the multi-speed transmission in accordance with the invention, thefirst shaft 1 is connectable through the first shifting element K1designed as a clutch and through the third shaft 3 to the planetary gearcarrier PT1 of the first planetary gear set RS1 and to the sun gear SR2of the second planetary gear set RS2, such that the planetary gearcarrier PT1 the first planetary gear set RS1 and the sun gear SR2 of thesecond planetary gear set RS2 are connected to each other, whereas theplanetary gear carrier PT1 of the first planetary gear set RS1 and thesun gear SR2 of the second planetary gear set RS2 are connectablethrough the third shaft 3 and through the sixth shifting element B2designed as a brake to the housing 11. Furthermore, the first shaft 1 isconnectable through the second shifting element K2 designed as a clutchand through the fourth shaft 4 to the ring gear HR1 of the firstplanetary gear set RS1. With the first design variant, the first shaft 1is connectable or connected through the third shifting element K3designed as a clutch and through the fifth shaft 5 both to the fixedgear 12 of the first spur gear stage ST1 and the planetary gear carrierPT2 of the second planetary gear set RS2. With the second designvariant, the first shaft 1 is connectable through the third shiftingelement K3 designed as a clutch, through the shaft 5 and through thefourth shifting element K4 designed as a clutch, and through the shaft9, to the idler gear 12A of the first spur gear stage ST1 and,furthermore, the first shaft 1 is connectable through the third shiftingelement K3 formed as a clutch and through the shaft 5 to the planetarygear carrier PT2 of the second planetary gear set RS2.

Regardless of the particular design variant, the second spur gear stageST2 is connected through the sixth shaft 6 to the ring gear HR3 of thethird planetary gear set RS3. In addition, the ring gear HR2 of thesecond planetary gear set 2 is connected through the seventh shaft 7 tothe planetary gear carrier PT3 of the third planetary gear set RS3.Moreover, the sun gear SR1 of the first planetary gear set RS1 and thesun gear SR3 of the third planetary gear set RS3 are connectable throughthe eighth shaft 8 and through the fifth shifting element B1 designed asa brake to the housing 11.

FIG. 3 shows a shifting diagram or a shifting matrix, as the case maybe, for the two equally effective transmission variants in accordancewith FIGS. 1 to 2. In the shifting diagram, for the realization of thevarious gears, shifting elements K1, K2, K3, K4, B1, B2 to be locked oractivated, as the case may be, are shown in table form, whereas atransmission ratio i is indicated for each gear and the respective gearjump φ is indicated between different gears. In addition to the nineforward gears G1, G2, G3, G4, G5, G6, G7, G8, G9 and the specifiedreverse gear R, additional shifting combinations are indicated asalternative fourth forward gears M1, M2, M3. As a whole, it also arisesfrom the shifting diagram that the proposed multi-speed transmissionfeatures optimized transmission ratio sequences with low absolute andrelative rotational speeds and low torques for the planetary gear setsand shifting elements. In addition, good degrees of toothing efficiencyand low drag torques arise from the selected arrangements of the gearsets.

As preferred stationary transmission ratios, a value of approximatelyi₀=−1.634 can be used for the first planetary gear set RS1, a value ofapproximately i₀=−2.146 can be used for the second planetary gear setRS2, a value of approximately i₀=−3.600 can be used for the thirdplanetary gear set RS3. As the stationary transmission ratio, a value ofapproximately i_(ST1)=−1.328 is selected for the first spur gear stageST1, and a value of approximately i_(ST2)=−1.000 is selected for thesecond spur gear stage ST2. Moreover, it arises from the shiftingdiagram that, for shifting all gears G1, G2, G3, G4, G5, G6, G7, G8, G9,R, M1, M2 and M2, each of the three shifting elements is locked.

Specifically, it arises from the shifting diagram in accordance withFIG. 3 that, for the realization of the first forward gear G1, thesecond shifting element K2 designed as a clutch, the fourth shiftingelement K4 designed as a clutch and the fifth shifting element B1designed as a brake are locked or activated. For the shifting of thesecond forward gear G2, the first shifting element K1 designed as aclutch, the fourth shifting element K4 designed as a clutch and thefifth shifting element B1 designed as a brake are locked or activated.For the shifting of the third forward gear G3, the first shiftingelement K1 designed as a clutch, the second shifting element K2 designedas a clutch and the fourth shifting element K4 designed as a clutch arelocked or activated. For the shifting of the fourth forward gear G4, thefirst shifting element K1 designed as a clutch, the third shiftingelement K3 designed as a clutch and the fourth shifting element K4designed as a clutch are locked or activated. For the shifting of thefifth forward gear G5, the first shifting element K1 designed as aclutch, the second shifting element K2 designed as a clutch and thethird shifting element K3 designed as a clutch are locked or activated.For the shifting of the sixth forward gear G6, the first shiftingelement K1 designed as a clutch, the third shifting element K3 designedas a clutch and the fifth shifting element B1 designed as a brake arelocked or activated. For the shifting of the seventh forward gear G7,the second shifting element K2 designed as a clutch, the third shiftingelement K3 designed as a clutch and the fifth shifting element B1designed as a brake are locked or activated. For the shifting of theeighth forward gear G8, the third shifting element K3 designed as aclutch, the fifth shifting element B1 designed as a brake and the sixthshifting element B2 designed as a brake are locked or activated. For theshifting of the ninth forward gear G9, the second shifting element K2designed as a clutch, the third shifting element K3 designed as a clutchand the sixth shifting element B2 designed as a brake are locked oractivated. Finally, for the shifting of the reverse gear R, the secondshifting element K2 designed as a clutch, the fourth shifting element K4designed as a clutch and the sixth shifting element B2 designed as abrake are locked or activated.

With respect to the shifting combinations of the alternative fourthforward gears M1, M2, M3, it is provided that, for the shifting of thealternative fourth forward gear M1, the third shifting element K3designed as a clutch, the fourth shifting element K4 designed as aclutch and the sixth shifting element B2 designed as a brake are lockedor activated. For the shifting of the alternative fourth forward gearM2, the third shifting element K3 designed as a clutch, the fourthshifting element K4 designed as a clutch and the fifth shifting elementB2 designed as a brake are locked or activated. Furthermore, for theshifting of the alternative fourth forward gear M3, the second shiftingelement K2 designed as a clutch, the third shifting element K3 designedas a clutch and the fourth shifting element K4 designed as a clutch arelocked or activated.

Modifications and variations can be made to the embodiments illustratedor described herein without departing from the scope and spirit of theinvention as set forth in the appended claims.

REFERENCE SIGNS

-   1 First shaft as a drive-   2 Second shaft as an output-   3 Third shaft-   4 Fourth shaft-   5 Fifth shaft-   6 Sixth shaft-   7 Seventh shaft-   8 Eighth shaft-   9 Ninth shaft-   11 Housing-   K1 First shifting element as a clutch-   K2 Second shifting element as a clutch-   K3 Third shifting element as a clutch-   K4 Fourth shifting element as a clutch-   B1 Fifth shifting element as a brake-   B2 Sixth shifting element as a brake-   RS1 First planetary gear set-   RS2 Second planetary gear set-   RS3 Third planetary gear set-   SR1 Sun gear of the first planetary gear set-   PT1 Planetary gear carrier of the first planetary gear set-   HR1 Ring gear of the first planetary gear set-   SR2 Sun gear of the second planetary gear set-   PT2 Planetary gear carrier of the second planetary gear set-   HR2 Ring gear of the second planetary gear set-   SR3 Sun gear of the third planetary gear set-   PT3 Planetary gear carrier of the third planetary gear set-   HR3 Ring gear of the third planetary gear set-   ST1 Machine element (first spur gear stage)-   ST2 Machine element (second spur gear stage)-   12 Fixed gear of the first spur gear stage-   12A Idler gear of the first spur gear stage-   13 Idler gear of the first spur gear stage-   13A Fixed gear of the first spur gear stage-   14 Fixed gear of the second spur gear stage-   15 Fixed gear of the second spur gear stage-   G1 First forward gear-   G2 Second forward gear-   G3 Third forward gear-   G4 Fourth forward gear-   G5 Fifth forward gear-   G6 Sixth forward gear-   G7 Seventh forward gear-   G8 Eighth forward gear-   G9 Ninth forward gear-   R Reverse gear-   M1 Alternative fourth gear-   M2 Alternative fourth gear-   M3 Alternative fourth gear-   i Transmission ratio-   i₀ Stationary transmission ratios of the planetary gear sets-   I_(ST1) Stationary transmission ratio of the first spur gear stage-   I_(ST2) Stationary transmission ratio of the second spur gear stage-   φ Gear jump

The invention claimed is:
 1. A planetary multi-speed transmission for avehicle, comprising: a housing (11); a first shaft (1) provided as adrive (An), and a second shaft (2) provided as an output (Ab) arrangedaxially parallel to the drive (An); a first planetary gear set, a secondplanetary gear set, and a third planetary gear set (RS1, RS2, RS3);additional shafts (3, 4, 5, 6, 7, 8, 9); six shifting elements (K1, K2,K3, K4, B1, B2), through which actuation of several gears are realized;a first machine element (ST1) and a second machine element (ST2)provided for transfer of torque between the drive (An) and the output(Ab); the first shaft (1) is connectable, as drive (An) to a planetarygear carrier (PT1) of the first planetary gear set (RS1), to a sun gear(SR2) of the second planetary gear set (RS2), to a ring gear (HR1) ofthe first planetary gear set (RS1), to a planetary gear carrier (PT2) ofthe second planetary gear set (RS2) and to the first machine element(ST1); and the second shaft (2), as an output shaft (Ab), is connectedor connectable to the first machine element (ST1) and to the secondmachine element (ST2); wherein the first shaft (1) is connectablethrough a first shifting element (K1) designed as a clutch and through athird shaft (3) to the planetary gear carrier (PT1) of the first plantar gear set (RS1) and to a sun gear (SR2) of the second planetary gearset (RS2), and wherein the planetary gear carrier (PT1) of the firstplanetary gear (RS1) and the sun gear (SR2) of the second planetary gearset (RS2) are connected to each other.
 2. The planetary multi-speedtransmission according to claim 1, wherein the first and the secondmachine elements are defined as spur gear stages (ST1, ST2) or chains.3. The planetary multi-speed transmission according to claim 2, whereinthe first shaft (1) is connectable through a third shifting element (K3)designed as a clutch and through a fifth shaft (5) both to a fixed gear(12) of the first spur gear stage (ST1) and the planetary gear carrier(PT2) of the second planetary gear set (RS2).
 4. The planetarymulti-speed transmission according to claim 2, wherein the second shaft(2) is connected to a fixed gear (15) of the second spur gear stage(ST2), and that the second shaft (2) is connectable through a fourthshifting element (K4) designed as a clutch and through a ninth shaft (9)to an idler gear (13) of the first spur gear stage (ST1).
 5. Theplanetary multi-speed transmission according to claim 2, wherein thesecond shaft (2) is connected to a fixed gear (13A) of the first spurgear stage (ST1) and to a fixed gear (15) of the second spur gear stage(ST2), and that an idler gear (12A) of the first spur gear stage (ST1)is connectable through a ninth shaft (9), through a fourth shiftingelement (K4) designed as a clutch, through a fifth shaft (5), andthrough a third shifting element (K3) designed as a clutch to the firstshaft (1).
 6. The planetary multi-speed transmission according to claim5, wherein the idler gear (12A) of the first spur gear stage (ST1) isconnectable through the ninth gear (9), through the fourth shiftingelement (K4) designed as a clutch, and through the fifth shaft (5) tothe planetary gear carrier (PT2) of the second planetary gear set (RS2).7. The planetary multi-speed transmission according to claim 2, whereina fixed gear (14) of the second spur gear stage (ST2) is connectedthrough a sixth shaft (6) to a ring gear (HR3) of the third planetarygear set (RS3).
 8. The planetary multi-speed transmission according toclaim 1, wherein the planetary gear carrier (PT1) of the first planetarygear set (RS1) and the sun gear (SR2) of the second planetary gear set(RS2) are connectable through the third shaft (3) and through a sixthshifting element (B2) designed as a brake to the housing (11).
 9. Theplanetary multi-speed transmission according to claim 1, wherein thefirst shaft (1) is connectable through a second shifting element (K2)designed as a clutch and through a fourth shaft (4) to a ring gear (HR1)of the first planetary gear set (RS1).
 10. The planetary multi-speedtransmission according to claim 1, wherein a ring gear (HR2) of thesecond planetary gear set (RS2) is connected through a seventh shaft (7)to a planetary gear carrier (PT3) of the third planetary gear set (RS3).11. The planetary multi-speed transmission according to claim 1, whereina sun gear (SR1) of the first planetary gear set (RS1) and a sun gear(SR3) of the third planetary gear set (RS3) are connectable through aneighth shaft (8) and through a fifth shifting element (B1) designed as abrake to the housing (11).
 12. The planetary multi-speed transmissionaccording to claim 1, wherein the shifting elements (K1, K2, K3, K4, B1,B2) are frictional-locking or positive-locking shifting elements. 13.The planetary multi-speed transmission according to claim 1, wherein thetransmission is shiftable to at least nine forward gears (G1 to G9) andat least one reverse gear (R).
 14. The planetary multi-speedtransmission according to claim 13, wherein: for shifting of a firstforward gear (G1), a second shifting element (K2) designed as a clutch,a fourth shifting element (K4) designed as a clutch, and a fifthshifting element (B1) designed as a brake are actuated; for shifting ofa second forward gear (G2), a first shifting element (K1) designed as aclutch, the fourth shifting element (K4) designed as a clutch, and thefifth shifting element (B1) designed as a brake are actuated; forshifting of a third forward gear (G3), the first shifting element (K1)designed as a clutch, the second shifting element (K2) designed as aclutch, and the fourth shifting element (K4) designed as a clutch areactuated; for shifting of a fourth forward gear (G4), the first shiftingelement (K1) designed as a clutch, a third shifting element (K3)designed as a clutch, and the fourth shifting element (K4) designed as aclutch are actuated; for shifting of a fifth forward gear (G5), thefirst shifting element (K1) designed as a clutch, the second shiftingelement (K2) designed as a clutch, and the third shifting element (K3)designed as a clutch are actuated; for shifting of a sixth forward gear(G6), the first shifting element (K1) designed as a clutch, the thirdshifting element (K3) designed as a clutch, and the fifth shiftingelement (B1) designed as a brake are actuated; for shifting of a seventhforward gear (G7), the second shifting element (K2) designed as aclutch, the third shifting element (K3) designed as a clutch, and thefifth shifting element (B1) designed as a brake are actuated; forshifting of an eighth forward gear (G8), the third shifting element (K3)designed as a clutch, the fifth shifting element (B1) designed as abrake, and a sixth shifting element (B2) designed as a brake areactuated; for shifting of a ninth forward gear (G9), the second shiftingelement (K2) designed as a clutch, the third shifting element (K3)designed as a clutch, and the sixth shifting element (B2) designed as abrake are actuated; and for shifting of a reverse gear (R), the secondshifting element (K2) designed as a clutch, the fourth shifting element(K4) designed as a clutch, and the sixth shifting element (B2) designedas a brake are actuated.
 15. The planetary multi-speed transmissionaccording to claim 14, wherein for shifting of alternative fourthforward gears (M1, M2, M3): the third shifting element (K3) designed asa clutch, the fourth shifting element (K4) designed as a clutch, and thesixth shifting element (B2) designed as a brake are actuated; the thirdshifting element (K3) designed as a clutch, the fourth shifting element(K4) designed as a clutch, and the fifth shifting element (B1) designedas a brake are actuated; or the second shifting element (K2) designed asa clutch, the third shifting element (K3) designed as a clutch, and thefourth shifting element (K4) designed as a clutch are actuated.